Lever drag type dual-bearing reel

ABSTRACT

A reel unit of the dual-bearing reel configured to support a spool, a spool shaft, a drag mechanism, and the drag adjusting lever. The reel unit has a first end member with a first opening and a first escape portion. The first opening accommodates a first flange portion and has an edge surface with a first facing portion facing towards the outer peripheral surface of the first flange portion. The first facing portion and the outer peripheral surface of the first flange portion define a gap with an axial length shorter than the axial length of the outer peripheral surface of the first flange portion. The first escape portion is arranged within the inner peripheral surface of the first end member and has a diameter larger than the first facing portion.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims priority under 35 U.S.C. §119 to Japanese Patent Application No. 2008-178488 filed on Jul. 8, 2008. The entire disclosure of Japanese Patent Application No. 2008-178488 is hereby incorporated herein by reference.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a fishing reel, more particularly, a lever drag type dual-bearing reel contrived to wind a fishing line about an axis oriented crosswise with respect to a longitudinal direction of a fishing rod.

2. Background Information

A reel unit of a lever drag type dual-bearing reel is provided with an opening in which a pair of flange portions of a spool is arranged. A gap between the opening and an external circumferential surface of each of the flange portions is made to be very small in order to prevent the fishing line from entering the gap and becoming tangled onto the spool shaft. The opening is longer than the external circumferential surface of the flange portions (e.g., Japanese Laid-Open Patent Publication No. 2003-250406). Consequently, the fishing line does not readily enter into the gap when it rides past the external circumferential surface of one of the flange portions. In particular, in a lever drag type dual-bearing reel, a storage space for housing a friction disk is formed in an outside face of a flange portion. Consequently, the length of the external circumferential surface of the flange portion on the friction disk side is longer than that of the flange portion on the opposite side and, thus, the length of the gap on the friction disk side is longer.

SUMMARY OF THE INVENTION

It has been discovered that in conventional lever drag type dual-bearing reel, as described above, the length of the gap between the opening and the external circumferential surface of the flange portion is longer on the friction disk side of the reel, making it more difficult for a fishing line to enter into the gap. However, if seawater or another liquid enters the gap, then the liquid will accumulate in the gap due to surface tension occurring at both the opening and the external circumferential surface of the flange portion. If liquid accumulates in the gap, then friction between the liquid and the flange portion will generate a resistance that inhibits the ability of the spool to freely rotate. When the ability of the tackle to rotate is inhibited, the casting distance decreases and there is the possibility that it will not be able to quickly arrange the tackle at a depth level where fish are concentrated when jigging.

Accordingly, aspects of the present invention have been created to solve the above-mentioned problems occurring in the conventional practice, and to prevent the fishing line from entering into the gap between the opening and the external circumferential surface of the flange portion to the greatest extent possible while also preventing liquid that enters the gap from inhibiting the ability of the spool to freely rotate.

According to one aspect of the present invention, a lever drag type dual-bearing reel lever is constructed to wind a fishing line around an axis transverse to a longitudinal direction of a fishing rod. The lever drag type dual-bearing reel comprises a spool, a spool shaft, a drag mechanism, a drag adjusting lever, and a reel unit. The spool includes a line winding body portion constructed to have a fishing line wound around the outer peripheral surface of the spool, and a first cylindrical flange portion and a second cylindrical flange portion arranged on opposite ends of the line winding body portion. The diameter of the first and the second cylindrical flange portions is larger than the diameter of the line winding body portion. The spool shaft is configured and arranged to rotatably support the spool. The drag mechanism includes a brake disk that cannot rotate in a line reel-out direction, a friction disk attached to the first flange portion and constructed to rotate integrally with the spool so as to engage and disengage from the brake disk, and a moving mechanism configured to move the friction disk along the axial direction of the spool shaft relative to the brake disk. The drag adjusting lever is configured to rotate about the spool shaft and arranged to adjust a drag force produced by the drag mechanism by controlling the moving mechanism. The reel unit supports the spool, the spool shaft, the drag mechanism, and the drag adjusting lever. The reel unit includes a first end member with a first escape portion and a second end member with a second escape portion. The first end member has a first opening to receive the first flange portion. The first opening has an edge surface with a first facing portion facing towards the outer peripheral surface of the first flange portion. The first facing portion and the outer peripheral surface of the first flange portion define a gap having an axial length shorter than the axial length of the outer peripheral surface of the first flange portion. The first escape portion has a diameter larger than the first facing portion and arranged within the inner peripheral surface of the first end member. The second end member is arranged opposite to the first end member and has a second opening to receive the second flange portion. The second opening has an edge surface with a second facing portion facing towards the outer peripheral surface of the second flange portion. The second facing portion and the outer peripheral surface of the second flange portion define a gap having an axial length shorter than the axial length of the outer peripheral surface of the second flange portion. The second escape portion having a diameter larger than the second facing portion and arranged within the inner peripheral surface of the second end member.

According to another aspect of the present invention, the reel unit further includes a third escape portion having a diameter larger than and arranged axially inward of the first facing portion, and a fourth escape portion having a diameter larger than arranged axially inward of the second facing portion.

According to still another aspect of the present invention, the diameter of the first flange portion is larger than the diameter of the second flange portion, and the diameter of the first opening is larger than the diameter of the second opening.

According to yet another aspect of the present invention, the outer peripheral surface of the first cylindrical flange portion is longer in the axial direction than the outer peripheral surface of the second flange portion, and the first cylindrical flange portion define a storage space to accommodate the friction disk and the brake disk.

According to still a further aspect of the present invention, the drag mechanism further includes a cover member configured and arranged to cover the storage space.

These and other features, aspects and advantages of the present invention will become apparent to those skilled in the art from the following detailed description, which, taken in conjunction with the annexed drawings, disclose example embodiments of the present invention.

BRIEF DESCRIPTION OF THE DRAWINGS

Referring now to the attached drawings which form a part of this original disclosure:

FIG. 1 is a perspective view of dual-bearing reel in which an embodiment of the present invention is employed;

FIG. 2 is a side view of the handle side of the same dual-bearing reel;

FIG. 3 is a cross sectional view of the same dual-bearing reel;

FIG. 4 is an exploded perspective view of a drag adjusting mechanism;

FIG. 5 is an enlarged cross sectional view showing constituent features of parts on the handle side;

FIG. 6 is an exploded perspective view showing constituent features of a rotation transmission system that includes a drag mechanism;

FIG. 7 is a cross sectional view focusing on specific portions surrounding a spool;

FIG. 8 is a frontal view of a cam member;

FIG. 9 is a cross sectional view of the cam member;

FIG. 10 is a development view depicting a circular arc-shaped cam surface in a linear fashion; and

FIG. 11 is an exploded perspective view of the spool sound generating mechanism.

DETAILED DESCRIPTION OF AN EXAMPLE EMBODIMENT

Selected embodiments of the present invention will now be explained with reference to the drawings. It will be apparent to those skilled in the art from this disclosure that the following descriptions of the embodiments of the present invention are provided for illustration only and not for the purpose of limiting the invention as defined by the appended claims and their equivalents.

Referring initially to FIGS. 1 to 3, a dual-bearing reel is illustrated in accordance with an example embodiment of the present invention. As shown in FIGS. 1 to 3, the dual-bearing reel is a small lever drag reel configured to wind a fishing line about an axis oriented crosswise with respect to a longitudinal direction of a fishing rod. The dual-bearing reel comprises a reel unit 1, a drag adjusting mechanism 7 including a drag adjusting lever 2 rotatably arranged on a side portion of the reel unit 1, a handle 3 rotatably supported on the reel unit 1 in a position below the drag adjusting lever 2, and a spool 4 arranged inside the reel unit 1. The dual bearing reel further comprises a spool shaft 5 arranged and configured to rotatably support the spool 4 and a drag mechanism 6 contrived to brake rotation of the spool 4 in a line reel-out direction.

Constituent Features of the Reel Unit

The reel unit 1 is a metal member made of, for example, an aluminum alloy. The reel unit 1 has a frame 10 and a first side plate 13 a and a second side plate 13 b arranged and configured to cover both sides of the frame 10. In this embodiment, the second side plate 13 b is formed as a one-piece integral unit with the frame 10, but it is acceptable for the second side plate 13 b to be a separate entity fastened to the frame 10. The frame 10 has a first cylindrical portion 11 a on a handle 3 side thereof, a second cylindrical portion 11 b that is smaller in diameter than the first cylindrical portion 11 a and arranged to be spaced apart from the first cylindrical portion 11 a along an axial direction of the spool shaft, and a plurality of connecting portions 12 a to 12 c arranged and configured to connect the cylindrical portions 11 a and 11 b together at frontward, rearward, and lower portions thereof. The external diameter of the first cylindrical portion 11 a is, for example, from 110% to 140% of the external diameter of the second cylindrical portion 11 b. In this embodiment, the external diameter of the first cylindrical portion 11 a is from 110% to 120% of the external diameter of the second cylindrical portion 11 b. The connecting portions 12 a to 12 c are formed as an integral unit with the first an second cylindrical portions 11 a and 11 b and, as shown in FIGS. 1 and 3, a metal rod mounting leg 8 a is fixed to the lower connecting portion 12 c. The rod mounting leg 8 a extends in a longitudinal direction of a fishing rod RD and is employed in order to mount the reel to the rod RD. A rod clamp 8 b is arranged opposite the rod mounting leg 8 a such that the fishing rod RD is sandwiched in-between.

As shown in FIGS. 1 to 3, the first side plate 13 a includes a cylindrical portion 14 that attaches to a side of the first cylindrical portion 11 b and a bulged portion 15 configured to protrude outward along an axial direction of the cylindrical portion 14 (to the right in FIG. 2). As shown in FIGS. 1 and 3, the second side plate 13 b is substantially circular in a side view and is integrally formed on a side of the second cylindrical portion 11 b. The cylindrical portion 14 and the second side plate 13 b are both substantially circular in a side view and each has approximately the same diameter as the first cylindrical portion 11 a and the second cylindrical portion 11 b, respectively. The external diameter of the first side plate 13 a is larger than the external diameter of the second side plate 13 b. The external diameter of the cylindrical portion 14 is, for example, from 110% to 140% of the external diameter of the second cylindrical portion 11 b. In this embodiment, the external diameter of the first cylindrical portion 14 is from 110% to 120% of the external diameter of the second cylindrical portion 11 b.

The bulged portion 15 is formed as an integral unit with the cylindrical portion 14 and is formed to protrude outward in an axial direction (rightward in FIG. 2) so as to contain a space that communicates with the cylindrical portion 14. The bulged portion 15 is a generally water droplet-shaped member having a smaller arc section above and a larger arc section below. The larger arc section protrudes downward beyond the cylindrical portion 14. The drag adjusting lever 2 and the handle 3 are mounted to the bulged portion 15 so as to be exposed to the outside.

As shown in FIGS. 4 and 5, the portion of the bulged portion 15 where the drag adjusting lever 2 is mounted is formed into a boss 34 for rotatably supporting the drag adjusting lever 2 and supporting the spool shaft 5. The boss 34 protrudes outward in a step-like fashion beyond other portions. The boss portion 34 has a large diameter protruding portion 34 a and a small diameter protruding portion 34 b that protrudes from the large diameter protruding portion 34 a. A bearing 20 d (explained later, see FIG. 5) is housed inside the large diameter protruding portion 34 a. A guide member 17 for supporting a cam member 50 (explained later, see FIG. 5) such that the cam member 50 cannot rotate but can move in an axial direction is fixed inside the boss 34, i.e., more specifically, inside the small diameter protruding portion 34 b.

The guide member 17 is crimp-fastened to the inside of the small diameter protruding portion 34 b such that it passes through the first side plate 13 a. The spool shaft 5 of the first side plate 13 a passes through the smaller diameter protruding portion 34 b. An outer peripheral surface of the guide member 17 is formed into a hexagonal guide section 17 a, and an internal surface is formed into a through hole 17 b configured such that the spool shaft 5 can pass there-through. A stopper 35 serving to establish a maximum drag position of the drag adjusting lever 2 is fixed to the bulged portion 15 in a position forward of the boss 34. The stopper 35 is arranged to touch against a lever portion 47 b (explained later) of the drag adjusting lever 2 so as to restrict rotation of the drag adjusting lever 2 in a clockwise direction (clockwise from the perspective shown in FIG. 2).

Constituent Features of the Rotation Transmission System

A outwardly protruding cylinder 16 for mounting the handle 3 is formed on the bulged portion 15 in a position below the drag adjusting lever 2. As shown in FIGS. 3 and 5, a cylindrical handle shaft 31 is arranged inside the protruding cylinder 16 so as to be parallel to the spool shaft 5 (which is a shaft about which the spool 4 rotates). The handle shaft 31 is rotatably supported in the protruding cylinder 16 with two bearings 32 and 33 arranged at both ends of the protruding cylinder 16 and is arranged such that one end thereof (left end in FIG. 5) protrudes axially inward beyond the bearing 32. A main gear 60 is rotatably attached to the end portion of the handle shaft 31 that protrudes beyond the bearing 32.

As shown in FIGS. 1 to 3, the handle 3 is fixed to the other end portion (distal end) of the handle shaft 31. The handle 3 has a handle arm 40 that is fixed to the distal end of the handle shaft 31 and a handle knob 41 that is rotatably supported on a distal end of the handle arm 40. The handle arm 40 is fastened to the distal end of the handle shaft 31 with a screw member 42 such that it can rotate as an integral unit with the handle shaft 31. In order to make it easier to grip and apply force to, the external shape of the handle knob 41 is formed to be rounded and generally T-shaped.

As shown in FIG. 5, the main gear 60 is prevented from rotating by a rotation preventing member 63 such that it rotates integrally with the handle shaft 31. The rotation preventing member 63 is connected to the handle shaft 31 such that it can rotate integrally there-with and is fastened the handle shaft 31 with a fastening bolt 65 screwed into to the proximal end of the handle shaft 31. The rotation preventing member 63 has a ring portion 63 a connected to the handle shaft 31 such that it can rotate integrally there-with and a pair of interlocking portions 63 b configured to interlock with the main gear 60. The interlocking portions 63 b are bent in an L-shaped fashion from the outer circumference of the ring portion 63 a and arranged on diametrically opposite sides of the ring portion 63 a. The main gear 60 is provided with a pair interlocking holes 60 a configured and arranged to interlock with the interlocking portions 63 b. The main gear 60 meshes with a pinion gear 61.

The pinion gear 61 is mounted onto the outside of the spool shaft 5 such that it can rotate about the spool shaft 5. The pinion gear 61 is rotatably supported with respect to the reel unit 1 by a bearing 20 d that is installed inside the large diameter protruding portion 34 a of the boss 34 of the first side plate 13 a. As shown in FIG. 6, gear teeth 61 a configured to mesh with the main gear 60 and a disk support portion 61 b formed to be generally rectangular are provided on an external circumferential surface of the pinion gear 61. Machining scars left by a gear cutting tool when the gear teeth 61 a were made remain on the disk support portion 61 b. An internal circumferential surface of the pinion gear 61 forms a through hole 61 c configured for the spool shaft 5 to pass through. An internal circumferential portion of a brake disk 22 (described later) of the drag mechanism 6 is connected to the disk support portion 61 b of the pinion gear 61 such that it can rotate integrally therewith. As a result, rotation of the handle 3 is transmitted to the friction disk 21 through the main gear 60, the pinion gear 61, and the brake disk 22. The friction disk 21 transfers the rotation to the spool 4 and the spool 4 rotates. A spring support plate 69 of a second one-way clutch 64 (explained later) is also mounted to the disk support portion 61 b such that it can rotate integrally therewith.

Constituent Features of the Spool Shaft and Surrounding Parts

As shown in FIG. 3, the spool shaft 5 is a shaft member supported on the reel unit 1 such that it can move in an axial direction but cannot rotate relative to the reel unit 1. An end of the spool shaft 5 depicted as the left end in FIG. 3 is supported in a boss 13 c formed in a center portion of the second side plate 13 b. The boss 13 c protrudes in an inward direction and the left end of the spool shaft 5 is supported therein such that it can move in an axial direction but cannot rotate relative to the boss 13 c. A rotation preventing pin 5 a for preventing the spool shaft 5 from rotating is arranged to pass through the spool 5 at a position closer to the left end of the spool shaft 5. The rotation preventing pin 5 a engages with a rotation preventing groove 13 d formed in the boss 13 c.

Bearings 20 a and 20 b for rotatably mounting the spool 4 and a bearing 20 c for rotatably supporting the brake disk 22 are attached to the outside circumference of the spool shaft 5.

Constituent Features of the One-way Clutches

As shown in FIG. 5, a roller type first one-way clutch 62 is arranged between the bearings 32 and 33. The first one-way clutch 62 only allows forward rotation of the handle shaft 31 in the line winding direction and prohibits reverse rotation in the line reel-out direction. A pawl type second one-way clutch 64 is arranged on the outer circumference of the spool shaft 5. The second one-way clutch 64 prevents reverse rotation of the handle shaft 31 by acting on the pinion gear 61.

The first and second one-way clutches 62 and 64 are used chiefly for operating the drag mechanism 6. As shown in FIG. 6, the second one-way clutch 64 has a ratchet wheel 66 connected to the brake disk such that it can rotate integrally therewith, a ratchet pawl 67 configured to engage with the ratchet wheel 66, an spring member 68 arranged to apply a spring force to the ratchet pawl 67, and a spring support plate 69 for mounting the spring member 68.

The ratchet wheel 66 is a plate-like member, an external circumferential surface of which is formed to have generally saw-like ratchet teeth 66 a configured to mesh with the ratchet pawl 67, and a radially inward portion of which is provided with an engaging protrusion 66 b configured to engage with the brake disk 22. The engaging protrusion 66 b is connected to an end face of a core member 25 (explained later) of the brake disk 22 such that it can rotate integrally therewith.

The ratchet pawl 67 is rotatably supported on a pivot shaft 90 that is screwed into an inside surface of the first side plate 13 a. At a proximal end thereof the ratchet pawl 67 has a pivot support portion 67 b provided with a support hole 67 a configured to be supported on the pivot shaft 90, and at a distal end thereof the ratchet pawl 67 has a pawl portion 67 c configured to mesh with the ratchet teeth 66 a of the ratchet wheel 66. An engaging slot 67 d configured to engage with the spring member 68 is formed in a middle portion of the ratchet pawl 67. Due to the spring action of the spring member 68, the ratchet pawl 67 pivots between a contact position in which it contacts the ratchet wheel 66 and prohibits rotation of the ratchet wheel 66 and a separated position in which it is separated from the ratchet wheel 66 so as to reduce the sound of the ratchet wheel 66 rotating in the line winding direction. The separated position of the ratchet pawl 67 is restricted to a position only slightly separated from the ratchet wheel 66 by a restricting part (not shown) provided on an inside surface of the first side plate 13 a.

The spring member 68 serves both to separate the ratchet pawl 67 from the ratchet wheel 66 when the spool 4 rotates in the line winding direction so as to quiet the sound of the second one-way clutch 64 and to force the ratchet pawl 67 toward the ratchet wheel 66 when the spool 4 rotates in the line reel-out direction. The spring member 68 is made of a metal wire material having a spring quality and is arranged such that it spring loads the ratchet pawl 67 in a different direction depending on the direction in which the spool 4 rotates. The spring member 68 is has a C-shaped mounting portion 68 a configured to engage frictionally with a mounting groove 69 a of the spring support plate 69, an arm portion 68 b that extends in a radial direction from the mounting portion 68 a, and a curved portion 68 c that is bent from the arm portion 68 b and configured to curve in a U-shaped manner and engage with the engaging slot 67 d. When the spool 4 rotates in the line winding direction and the brake disk 22 rotates in the same direction, the spring member 68 applies a spring force against the ratchet pawl 67 in a direction of separating from the ratchet wheel 66. Conversely, when the spool 4 rotates in the line reel-out direction and the brake disk 22 rotates in the same direction, the spring member 68 applies a spring force against the ratchet pawl 67 in a direction of moving closer to the ratchet wheel 66. As a result, rotation of the brake disk 22 in the line reel-out direction is prevented.

The spring support plate 69 is a circular disk shaped member having a mounting groove 69 a configured to frictionally engage with the mounting portion 68 a of the spring member 68 formed in an external circumferential surface thereof. In a radially inward portion of the spring support plate 69 there is formed a rectangular connecting hole 69 b configured to connect to the disk support portion 61 b of the pinion gear 61 such that the spring support plate 69 can rotate integrally with the pinion gear 61.

Constituent Features of the Spool

As shown in FIG. 7, the spool 4 comprises a spool unit 9 and a fishing line stop pin 23 that is fixed to the spool body 9. The spool unit 9 has a cylindrical line winding body portion 9 a that is configured for a fishing line to be wound onto an outside circumferential surface thereof and arranged such that a gap exists between an internal circumferential surface thereof and an external circumferential surface of the spool shaft 5. The spool unit 9 also has a first flange portion 9 b and a second flange portion 9 c that are larger in diameter than the line winding body portion 9 a and arranged on both sides of the line winding body portion 9 a. The spool unit 9 also has a counterbored portion 9 f formed in the outside circumferential surface of the line winding body portion 9 a and a pin fixing portion 9 h formed in the counterbored portion 9 f.

The spool unit 9 is rotatably supported on the spool shaft 5 with bearings 20 a and 20 b. The drag mechanism 6 is provided on the handle 3 side of the spool 4. A spool sound generating mechanism 18 contrived to generate a sound when the spool 4 rotates is provided on the second side plate 13 b side of the spool 4.

As shown in the partial view G of FIG. 7, the counterbored portion 9 f is a circular recess formed in the external circumferential surface of the line winding body portion 9 a at a middle position with respect to an axial direction. A bottom surface 9 g of the counterbored portion 9 f is flat and the pin fixing portion 9 h—which has a through hole 9 i is formed in a center of the bottom surface 9 g. The through hole 9 i is formed to pass from the bottom surface 9 g to the internal circumferential surface of the line winding body portion 9 a along a radial direction of the line winding body portion 9 a.

The fishing line stop pin 23 serves to hold an end of the fishing line and is secured by being press fitted into the through hole 9 i (which is positioned midway along the axial direction of the line winding body portion 9 a). The fishing line stop pin 23 has a first shaft portion 23 a configured to be press fitted into the through hole 9 i, a second shaft portion 23 b having a larger diameter than the first shaft portion 23 a and configured such that a fishing line can be held on an external circumferential surface thereof by, for example, tying the fishing line, and a head portion 23 c having a larger diameter than the second shaft portion 23 b.

Thus, the fishing line stop pin 23 is made to have a first shaft portion 23 a and a second shaft portion 23 b that is larger in diameter than the first shaft portion 23 a. The first shaft portion 23 a is configured to be press fitted into the through hole, and the counterbored portion 9 f is configured to have a flat bottom surface 9 g. Consequently, the press fitting of the fishing line stop pin 23 into the through hole 9 i can be ended when the step-like portion between the first shaft portion 23 a and the second shaft portion 23 b contacts the bottom surface 9 g, and the amount by which the fishing line stop pin 23 is pressed in can be held to a prescribed amount. Moreover, since the step-like portion contacts the flat bottom surface 9 g, it is more difficult for a gap to exist between the step-like portion and the bottom surface 9 g and more difficult for the fishing line to become pinched between the step-like portion and the bottom surface 9 g.

The first flange portion 9 b is larger in diameter than the second flange portion 9 c, and the axial length of an external circumferential surface 9 d is longer than the axial length of an external circumferential surface 9 e of the second flange portion 9 c. A storage space 36 configured such that the drag mechanism 6 can be stored therein is formed in an outside face of the first flange portion 9 b.

The first flange portion 9 b is inserted into the first cylindrical portion 11 a, and the second flange portion 9 c is inserted into the second cylindrical portion 11 b. The first cylindrical portion 11 a has a circular first opening 19 a configured such that the first flange portion 9 b can be inserted therein. The first cylindrical portion 11 a has a first facing portion 19 c that is provided at the edge of the first opening 19 a, faces toward the external circumferential surface of the first flange portion 9 b at the edge of the opening such that it forms only a small gap (e.g., 0.2 to 0.7 mm) therewith, and is shorter in length than the external circumferential surface of the first flange portion 9 b. The first cylindrical portion 11 a also has a first escape portion 19 e arranged farther outward along the axial direction of the spool shaft than the first facing portion 19 c and having a larger diameter than the first facing portion 19 c. Additionally, the first cylindrical portion 11 a has a first escape portion 19 e arranged on an inward side of the first facing portion 19 c along an axial direction of the spool shaft and having a larger diameter than the first facing portion 19 c. In this explanation, “inward along the axial direction of the spool shaft” means axially toward a middle portion of the spool unit 9 (i.e., the portion where the fishing line stop pin 23 is installed), and “outward along the axial direction of the spool shaft” means in an axial direction oriented away from the middle portion of the spool unit 9.

The second cylindrical portion 11 b has a circular second opening 19 b configured such that the smaller diameter second flange portion 9 c of the spool unit 9 can be inserted therein. Thus, the second opening 1 9 b has a smaller diameter than the first opening 19 a. As shown in FIG. 7, the second cylindrical portion 11 b has a second facing portion 19 d that is provided at the edge of the second opening 19 b, faces toward the external circumferential surface of the second flange portion 9 c at the edge of the opening such that it forms only a small gap (e.g., 0.2 to 0.7 mm) therewith, and is shorter in length than the external circumferential surface of the second flange portion 9 c. The second cylindrical portion 11 b also has a second escape portion 19 f arranged farther to the outside along the axial direction of the spool shaft than the second facing portion 19 d and having a larger diameter than the second facing portion 19 d. Additionally, the second cylindrical portion 11 b has a fourth escape portion 19 h arranged on an inward side of the second facing portion 19 d along the axial direction of the spool shaft and having a larger diameter than the second facing portion 19 d.

In this way, since the length of the portion where the first opening 19 a and the first flange portion 9 b (which is normally longer than the second flange portion 9 c) face each other is short, a liquid entering the gap there-between will flow more readily toward the first escape portion 19 e where the gap is wider. As a result, a liquid entering the gap between the first opening 19 a and the first flange portion 9 b will be less likely to inhibit the ability of the spool 4 to freely rotate.

Additionally, a first water drain hole 13 e is provided in a portion of the first cylindrical portion 11 a where the first escape portion 19 e is formed and a second water drain hole 13 f is provided in a portion of the second cylindrical portion 11 b where the second escape portion 19 f is formed. The water drain holes are formed in portions corresponding to the lower connecting portion 12 c. The first and second water drain holes 13 e and 13 f serve to discharge any liquid that enters the reel through the gap between the first flange portion 9 b and the first opening 19 a or the gap between the second flange portion 9 c and the second opening 19 b.

Constituent Features of the Drag Adjusting Mechanism

As shown in FIGS. 3 to 5, the drag adjusting mechanism 7 serves as a moving mechanism for moving the drag mechanism 6 in order to change and adjust a drag force applied against rotation of the spool 4 (which is mounted to the spool shaft 5) in the line reel-out direction. In FIGS. 3 and 5, the portion below the center axis X of the spool shaft 5 indicates an axial position of the spool shaft 5 when the drag adjusting mechanism 7 is set for maximum drag, and the portion above indicates an axial position of the same when the drag adjusting mechanism 7 is in a released state.

The drag adjusting mechanism 7 comprises a cam mechanism 43 contrived to convert rotation of the drag adjusting lever 2 into a movement of the drag mechanism 6 along an axial direction of the spool shaft, a rotation restricting portion 44 (see FIG. 10) provided in the cam mechanism 43 and contrived to restrict rotation of the drag adjusting lever 2, and a lever sound generating mechanism 45 contrived to generate a sound when the drag adjusting lever 2 is rotated.

Constituent Features of the Drag Adjusting Lever

The drag adjusting lever 2 is arranged such that the drag force increases when the drag adjusting lever 2 is rotated clockwise (clockwise from the perspective of FIG. 2) and decreases when the drag adjusting lever 2 is rotated counterclockwise. A position slightly clockwise of the position depicted with a solid-line sketch is a strike position, the position depicted with a double-dot chain line is a drag release position, and the position depicted with a broken line sketch is a maximum drag position. The strike position is a position that can be adjusted to a drag force at which the hook will pierce the fish's mouth securely but the fishing line will not break when a fish suddenly bites and pulls strongly. Typically it is set to approximately one-third of the breakage strength of the fishing line.

The drag adjusting lever 2 is rotatably attached to the external circumferential surfaces of the large diameter protruding portion 34 a and the small diameter protruding portion 34 b of the boss 34 of the first side plate 13 a. The drag adjusting lever 2 has a lever unit 47 made of, for example, an aluminum alloy and an insert member 48 configured to be press fitted into the lever unit 47 and made of, for example, a zinc alloy. The lever unit 47 has a proximal end portion 47 a arranged to surround the boss 34 and a lever portion 47 b that extends radially outward from the proximal end portion 47 a. A cut-out portion 47 c is diagonally formed in an internal circumferential surface of the proximal end portion 47 a at a portion bordering with the lever portion 47 b, and the lever sound generating mechanism 45 is installed therein. The insert member 48 is press fitted into an internal circumferential surface of the proximal end portion 47 a such that it is fixed therein.

The insert member 48 is a stepped cylindrical member rotatably supported on the large diameter protruding portion 34 a and the small diameter protruding portion 34 b. Two cam receiving pins 52 a constituting a cam receiving section 52 of the cam mechanism 4, for example, are erectly provided on an external circumferential surface of a small diameter cylindrical portion 48 a of the insert member 48 so as to extend along a radial direction. As shown in FIG. 4, a radial bush 46 a for rotatably supporting the insert member 48 is arranged between the small diameter cylindrical portion 48 a of the insert member 48 and the small diameter protruding portion 34 b of the boss 34. A thrust ring 46 b is installed so as to be axially supported between the insert member 48 and a wall surface 34 c of the boss 34.

Constituent Features of Lever Sound Generating Mechanism

The lever sound generating mechanism 45 serves to accomplish positioning of the drag adjusting lever 2 in addition to generating a sound when the drag adjusting lever 2 is operated. As shown in FIGS. 4 and 5, the lever sound generating mechanism 45 includes a cylindrical sound generating member 70 mounted on the external circumferential surface of the large diameter protruding portion 34 a of the boss 34 and a striker mechanism 71 contrived to repeatedly strike against the sound generating member 70.

The sound generating member 70 is a ring shaped member made of, for example, polyacetal or another synthetic resin that is comparatively hard and has an excellent sliding property. The sound generating member 70 has a cone-shaped surface 70 a that tapers to a smaller diameter as one move in an outward direction along an axial direction of the spool shaft 5, and an undulated portion 70 b formed along a circumferential direction of the cone-shaped surface 70 a. The undulated portion 70 b comprises circular arc-shaped recesses formed in the cone-shaped surface 70 a. The sound generating member 70 is installed on the large diameter protruding portion 34 a such that it cannot rotate, its movement in an axially inward direction is restricted, and its movement in an axially outward direction is unrestricted. Movement of the sound generating member 70 in the axially inward direction is restricted by an outside wall surface 15 a of a portion of the bulged portion 15 where the boss 34 is formed. A rotation preventing hole 15 b is formed in the outside wall surface 15 a, and a rotation preventing protrusion 70 c configured to engage with the rotation preventing hole 15 b is formed on the sound generating member 70. As a result, movement of the sound generating member 70 in the axially inward direction is restructured and the sound generating member 70 is prevented from rotating. However, movement of the sound generating member 70 in the axially outward direction is not restricted.

The lever sound generating mechanism 45 also has an installation portion 72 provided with an installation hole 72 a formed in the cut-out portion 47 c of the drag adjusting lever 2 along an axis substantially perpendicular to the cone-shaped surface 70 a. The striker mechanism 71 has a sounding pin 73 installed in the installation hole 72 a such that it can move back and forth toward and away from the cone-shaped surface 70 a and a coil-type spring member 74 installed in the installation hole 72 a such that it spring loads the sounding pin 73 toward the undulated portion 70 b. The sounding pin 73 is made of, for example synthetic resin material and configured such that distal end thereof is spherical and a proximal end thereof is smaller in diameter than the distal end. The spring member 74 is arranged on the outside circumference of a proximal end portion of the sounding pin 73.

Thus, in this embodiment, a sound generating member 70 is made to have a tapered cone-shaped surface 70 a whose diameter decreases along an axially outward direction, an undulated portion 70 b is formed on the cone-shaped surface 70 a, and a sounding pin 73 of a striker mechanism 71 is arranged and configured to contact the undulated portion 70 b in an elastic fashion. Since the striker mechanism 71 spring loads the sound generating member 70 in an axially inward direction, the sound generating member 70 is retained in place by the striker mechanism 71. As a result, the sound generating member 70 can be mounted to the boss 34 without providing a separate retaining structure.

Also, since the installation hole 72 a is formed along an axis substantially perpendicular to the cone-shaped surface 70 a, the sounding pin 73 spring loaded by the spring member can be 74 can serve to spring load the sound generating member 70 axially inward while allowing the sound generating member 70 to freely move in the axially outward direction. Thus, since sounding pin 73 spring loaded by the spring member 74 can spring load the sound generating member 70 axially inward, the striker member can serve to retain the sound generating member 70 in position. As a result, a clear clicking sound is generated and the sound generating member 70 can be retained more securely with the sounding pin 73.

Since the installation hole 72 a is formed diagonally, even if it is formed in a position close to an inward side surface of the drag adjusting lever 2, the distance between the installation hole 72 a and the inward side surface will gradually increase. As a result, the installation hole 72 a is less likely to cause a portion where the wall thickness is thin to exist in the drag adjusting lever 2 and the decrease in strength at the portion where the installation hole 72 a is made can be suppressed.

Once the sounding pin 73 is installed in the installation hole 72 a, it is difficult to remove. However, since the sounding pin 73 is made of a synthetic resin that does not readily corrode, the lever sound generating mechanism 45 is maintenance free because the sounding pin 73 will not corrode and become jammed in the installation hole 72 a.

Constituent Features of the Cam Mechanism

The cam mechanism 43 comprises a cam member 50, a drag adjusting knob 51, a cam receiving portion 52, and a first force applying member 53. The cam member has a cam surface 49. The drag adjusting knob 51 is for setting an adjustment range of the drag adjusting lever 2. The cam receiving portion 52 is arranged such that it can contact the cam surface 49 and serves to move the cam member 50 in a first axial direction (rightward in FIG. 5) when the drag adjusting lever 2 is rotated clockwise from the perspective FIG. 2. The first force applying member 53 is a coil spring serving to generate a spring force that acts through the drag adjusting knob 51 so as to move the cam member 50 in a second axial direction such that it contacts the cam receiving portion 52 when the drag adjusting lever 2 is rotated counterclockwise from the perspective of FIG. 2. The drag adjusting mechanism 7 has a second force applying member 54 that serves to spring load the spool 4 in a direction of separating from the spool shaft 5 (rightward in FIG. 3) and comprises, for example, four Belleville springs.

Constituent Features of the Cam Member

The cam member 50 is a cylindrical member made of, for example, a stainless metal alloy. As shown in FIGS. 8 and 9, the cam member 50 has an outer cylindrical portion 50 a, an inner cylindrical portion 50 b, and a disk portion 50 c that joins the outer cylindrical portion 50 a and the inner cylindrical portion 50 b together. The cam surface 49 is formed on an edge of the outer cylindrical portion 50 a. An annular groove 50 d configured for an O-ring 56 to be installed therein is formed in the outer cylindrical portion 50 a. An internal surface of the inner cylindrical portion 50 b is made into hexagonal hole 50 e configured to engage with the hexagonal guide section 17 a of the guide member 17. Sounding recesses 50 f forming part of a knob sound generating mechanism 55 (explained later) are formed in an outward surface of the disk portion 50 c.

As shown in FIGS. 8 and 10, the cam surface 49 is a slanted surface formed along an edge face of the cam member 50 in an overall circular arc-like shape and configured such that its protruding height gradually decreases. Two cam surfaces 49 having the same shape are formed at 180° intervals. A rotation restricting portion 44 configured to restrict rotation of the drag adjusting lever 2 is formed on both sides of a restriction position C located at an intermediate portion of the cam surface 49. The restriction position C is located, for example, 25° to 30° away from a reference position A of the cam surface 49.

The rotation restricting portion 44 has a restricting protrusion 44 a configured to protrude toward the cam receiving pin 52 a. The restricting protrusion 44 a has an apex 44 b positioned at the restriction position C, a first slanted surface 44 c that declines from the apex 44 b to a first position B equivalent to a drag release position, and a second slanted surface 44 d that declines from the apex 44 b in a direction opposite the first position B. A slant angle a of the first slanted surface 44 c is smaller than a slant angle β of the second slanted surface 44 d. The slant angle a is preferably larger than 10° and smaller than or equal to 18°, e.g., 14° in this embodiment. The second slanted surface 44 d is formed with a circular arc whose radius of curvature is substantially equal to a radius of curvature of a cam receiving pin 52 a, indicated in FIG. 10 with a double-dot chain line. The slant angle β of a tangential line intersecting at the apex 44 b is preferably larger than 18° and smaller than or equal to 25°, e.g., 20° in this embodiment. A first height H1 of the apex 44 b in an-axial direction of the spool shaft is smaller than one half of a second height H2 of the restricting protrusion 44 a at a second position E corresponding to a maximum drag position. In this embodiment, for example, the first height H1 of the apex 44 b is from 0.6 to 0.8 mm and the second height H2 of the second position E is from 1.7 to 2.0 mm. In this embodiment, the second position E is 150° from the reference position A.

The first slanted surface 44 c and the second slanted surface 44 d on both sides of the apex 44 b of the restricting protrusion 44 a are configured such that the slant angle a of the first slanted surface 44 c (which is on the drag release position side) is smaller than the slant angle β of the second slanted surface 44 d. Consequently, when the drag adjusting lever 2 is rotated from the maximum drag position side to the rotation restricting portion 44, before the restricting protrusion 44 is passed, the drag force increases and it becomes more difficult to rotate the drag adjusting lever 2 toward the drag release position. Conversely, when the drag adjusting lever 2 is rotated from the drag release position toward the rotation restricting portion 44, the change in the drag force is smaller and the rotation operation is easier to perform because the slope of the first slanted surface 44 c is more gradual.

Additionally, since the first height H1 of the apex 44 b in an axial direction of the spool shaft is smaller than one half of the second height H2 of the restricting protrusion 44 a at the second position E (which corresponds to a maximum drag position), the apex 44 b is located in a position corresponding to a movement amount of the spool shaft 5 that is less than one half of a maximum movement amount and, consequently, a small drag force can be made to act on the spool 4 when rotation is restricted.

The cam surface 49 includes a first flat surface 49 a, a second flat surface 49 b, and a third slanted surface 49 c. The first flat surface 49 a is formed from the first position B to the reference position A and arranged to be substantially perpendicular to the spool shaft. The second flat surface 49 b is formed from the second position E to a fourth position F, arranged to be parallel to the first flat surface 49 a, and configured to protrude more in an axial direction than the first flat surface 49 a. The third slanted surface 49 c joins the first flat surface 49 a and the second flat surface 49 b together. The restricting protrusion 44 a is formed between the first flat surface 49 a and the third slanted surface 49 c.

In this embodiment, the third slanted surface 49 c comprises a fourth slanted surface 49 d and a fifth slanted surface 49 e having different slant angles and bordering each other at a third position D located 100° from the reference position A. The slant angle γ of the fourth slanted surface 49 d is larger than 3° and equal to or smaller than 4°, and the slant angle δ of the fifth slanted surface 49 e is larger than 2° and equal to or smaller than 3° (which is smaller than that of the fourth slanted surface 49 d). A recessed portion 49 f that is slightly recessed (e.g., 0.05 to 0.2 mm) in a circular arc shape is formed at the third position D and serves to inform a user of the strike position. The recessed portion 49 f and the cam receiving pin 52 a are formed to have approximately the same radius of curvature. When the strike position is passed, the slant angle decreases and, thus, the rate of increase of the drag force decreases.

The angular distance from the reference position A to the fourth position F is, for example, 170°. A restricting wall 49 g arranged parallel to the spool shaft is formed at the fourth position F. A restricting wall 49 g serves to restrict the drag release position such that the drag adjusting lever 2 does not rotate beyond that position. However, if the aforementioned stopper 35 was not there, then the drag adjusting lever could be rotated beyond the restricting wall 49 g at the maximum drag position Thus, the stopper 35 serves to prevent the drag adjusting lever 2 from rotating beyond the maximum drag position. The restricting wall 49 g is also configured to have a circular arc-shaped surface having the same radius of curvature as the cam receiving pins 52 a.

Other Constituent Features of Cam Mechanism

As shown in FIGS. 4 and 5, the drag adjusting knob 51 is configured to screw onto an externally threaded portion 5 c formed on an end portion of the spool shaft 5. The drag force of the strike position and an adjustment range of the drag force can be adjusted by adjusting the amount by which the drag adjusting knob 51 is screwed in or out. A knob sound generating mechanism 55 contrived to generate a sound when the drag adjusting knob 51 is operated is provided inside the drag adjusting knob 51. The knob sound adjusting mechanism 55 comprises a sounding recess 50 f formed in the cam member 50, a sounding pin 55 a installed in a storage hole 51 a such that it can move toward and away from the sounding recess 50 f, and a spring member 55 b serving to spring load the sounding pin 55 a toward the sounding recess 5Of. The storage hole 51 a is formed in the drag adjusting knob 51 to be generally parallel to the spool shaft 5.

As described previously, the cam receiving portion 52 has two cam receiving pins 52 a erectly provided on an insert member 48 of the drag adjusting lever 2. The cam receiving pins 52 a are rod-like members made of, for example, a stainless metal alloy and are secured to an outside circumferential surface of the small diameter cylindrical portion 48 a of the insert portion 48 by press fitting, an adhesive, or other suitable fixing means. The cam receiving pins 52 a serve to move the cam member 50 while contacting the cam surface 49.

The first force applying member 53 is arranged on an outside circumference of the spool shaft 5 between the bearing 20 b and the bearing 20 c. The first force applying member 53 spring loads the spool 4 in a direction of separating from the drag mechanism 6 and causes the cam member 50 to contact the cam receiving portion 52. The second force applying member 54 is arranged on an outside circumference of the spool shaft 5 in a position axially outward (leftward in FIG. 3) from the bearing 20 a. The second force applying member 54 spring loads the spool 4 axially inward (rightward in FIG. 3) with respect to the spool shaft 5. The second force applying member 54 is arranged between the bearing 20 a and a retaining ring 5 b attached to the spool shaft 5. The first force applying member 53 applies a weaker force than the second force applying member 54. Consequently, when the spool shaft 5 moves axially rightward during a drag adjustment, the first force applying member 53 compresses first and the second force applying member 54 compresses next. The second force applying member 54 is provided in order to make the drag force change smoothly.

Constituent Features of the Drag Mechanism

The drag mechanism 6 is configured to move along an axial direction of the spool shaft 5 of the spool 4 and brake rotation of the spool 4 in the line reel-out direction. As shown in FIGS. 5 and 6, the drag mechanism 6 is housed inside a circular storage space 36 formed in the first flange portion 9 b side of the spool 4. The drag mechanism 6 comprises a friction disk 21 arranged such that it can rotate integrally with the spool unit 9, a brake disk 22 arranged facing opposite the friction disk 21, and a cover member 26 serving to cover the storage space 36 from the axially outward direction of the spool shaft 5.

The friction disk 21 is arranged inside the storage space 36 such that it contacts an outward facing surface of the first flange portion 9 b. The friction disk 21 is a circular disk-shaped member having at least one (e.g., four) engaging recess 21 a formed in an external circumferential surface thereof and recessed in a radially inward direction. The friction disk 21 is connected to the spool unit 9 by the cover member 26 such that it can rotate integrally with the spool unit 9. The friction disk 21 is made of a heat resistant synthetic resin material, such as a fiber reinforced resin material made by impregnating, for example, a woven cloth made of carbon fibers with a phenol resin or other heat resistant resin.

The cover member 26 is a bottomed cylindrical member having a cylindrical portion 26 a and a bottom portion 26 b and made of a metal material, e.g., an aluminum alloy. The cover member 26 is fastened to an end face of the first flange portion 9 b with a plurality of screw members 28 (see FIG. 5). The cover member 26 has a through hole 26 c provided in a center of the bottom portion 26 b through which the core member 25 of the brake disk 22 can pass. The cylindrical portion 26 a has an external circumferential surface 26 d configured to fit snugly inside an internal circumferential surface of the first flange portion 9 b, i.e., of the storage space 36. The length of the cylindrical portion 26 a in an axial direction of the spool shaft 5 is set such that when the cover member 26 is fastened to the first flange portion 9 b, the distal end of the cylindrical portion 26 can contact a side surface of the friction disk 21. A circular protruding portion 26 f is arranged to protrude from the external circumferential surface 26 d of the cylindrical portion 26 a and configured such that it can mate closely with an end face of the first flange portion 9 b. The protruding portion 26 f is arranged to face toward the end face of the first flange portion 9 b and has screw through holes 26 g that are configured for the screw members 28 (FIG. 7) to be installed through and arranged along a circumferential direction with spaces in-between. Threaded holes 9 j (FIG. 7) configured for the screw members 28 to screw into are formed in the end face of the first flange portion 9 b.

The cover member 26 has at least one engaging protrusion 26 e configured to engage with the engaging recess 21 a provided on a distal end surface of the cylindrical portion 26 a. The engaging protrusions 26 e (e.g., four) are formed on the distal end of the cylindrical portion 26 a and protrude axially toward an outward facing surface of the first flange portion 9 b. The engaging protrusions 26 e are circular arc-shaped and arranged to be spaced apart along a circumferential direction. The axially protruding length of the engaging protrusions 26 e is set such that a slight gap exists between the outward facing surface of the first flange portion 9 b and the distal end portions of the engaging protrusions 26 e.

The brake disk 22 is connected to the second one-way clutch 64 and is prohibited from rotating in the line reel-out direction. As shown in FIGS. 5 and 6, the brake disk 22 has donut-shaped sliding disk 24 arranged such that it can contact the friction disk 21 and a core member 25 that is mounted to the spool shaft 5 such that it cannot move axially but can freely rotate with respect to the spool shaft 5. The sliding disk 24 is made of stainless steel or another heat resistant, corrosion resistant metal material. The sliding disk 24 has a slightly smaller diameter than the friction disk 21 and is retained in place on the core member 25 by a retaining member 27. A rectangular engaging hole 24 a is provided in a center portion of the sliding disk 24. The engaging hole 24 a is configured to engage with the core member 25 such that the sliding disk can rotate integrally therewith.

The core member 25 is a generally cylindrical member made of, for example, an aluminum alloy. The core member 25 is rotatably supported on the spool shaft 5 with the aforementioned bearing 20 c. An internal surface of a pinion gear 61 side of the core member 25 is formed into a rectangular engaging hole 25 a (FIG. 5) configured to engage with the disk support portion 61 b of the pinion gear 61 such that the core member 25 can rotate integrally with the pinion gear 61. A coupling groove 25 b is formed in an end face of the core member 25 facing toward the pinion gear 61 along the direction of a diameter thereof. The coupling groove 25 b is configured to couple to the ratchet wheel 66 of the second one-way clutch 64 such that the ratchet wheel 66 can rotate integrally with the core member 25. More specifically, the engaging protrusions 66 b of the ratchet wheel 66 engage with the coupling groove 25 b such that the ratchet wheel 66 rotates integrally with the pinion gear 61 and the core member 25.

A generally rectangular rotation preventing portion 25 c for coupling to the sliding disk 24 in an integrally rotatable manner is formed on an external circumferential surface of the core member 25 on the opposite side as the pinion gear 61. The rotation preventing portion 25 c engages with an engaging hole 24 a (explained later) of the sliding disk 24 such that the core member 25 and the sliding disk 24 rotate as an integral unit. An annular groove 25 d for installing the retaining member 27 is formed in the rotation preventing portion 25 c. Also, an annular mounting groove 25 e for mounting a seal member 29 to seal an inside of the cover member 26 is formed in an external circumferential surface between the rotation preventing portion 25 c and the coupling groove 25 b. Since an internal surface of the core member 25 engages with the pinion gear 61, the pinion gear 61 is restrained from moving axially outward (rightward in FIG. 5) by the reel unit 1 through the bearing 20 d.

The seal member 29 has a lip 29 a on an outer periphery thereof. The lip 29 a is configured such that it does not contact the cover member 26 when the reel is in the drag released state shown in the portion of FIG. 5 drawn above the spool center axis X, and such that it contacts the cover member 26 and seals the inside thereof when the reel is in the maximum drag state shown in the portion of FIG. 5 drawn below the spool center axis X As a result, the resistance to rotation of the spool 4 can be decreased when the reel is in the drag released state and the spool is rotating freely.

When the drag mechanism 6 is assembled, the spool 4 is attached to the spool shaft 5 and then, for example, the brake disk 22 and the friction disk 21 are installed into the cover member 26. When this is done, the engaging protrusions 26 e of the cover member 26 are made to engage with the engaging recesses 21 a of the friction disk 21. Next, the spool shaft 5 is inserted and the protruding portion 26 f of the cover member 26 is made to mate closely with an end face of the first flange portion 9 b. If the protruding portion 26 f will not mate closely, then the engaging protrusions 26 e are not properly engaged with the engaging recesses 21 a and the engaging protrusions 26 e and the engaging recesses 21 a should be realigned and engaged with one another again. Finally, the screw through holes 26 g and the threaded holes 9 j are aligned with one another and screw members 28 are installed so as to fasten the cover member 26 to the first flange portion 9 b. In this way, the friction disk 21 is prevented from rotating with respect to the spool 4. As explained previously, it is easy to verify visually whether the engaging protrusions 26 e and engaging recesses 21 a are engaged with one another because a gap will exist between the protruding portion 26 f and the end face of the first flange portion 9 b if the engaging protrusions 26 e are not engaged with the engaging recesses 21 a. In this embodiment, the cover member 26—not the storage space 36—serves to prevent the friction disk 21 from rotating. Consequently, the cylindrical portion 26 a of the cover member 26 can be fit snugly into the storage space 36 and the size of the gap between the cover member 26 and the storage space 36 can be decreased. Furthermore, since the protruding portion 26 f mates closely with the end face of the first flange portion 9 b, the friction disk 21 can be prevented from rotating while allowing the storage space 36 to have a shape that is easier to seal.

Additionally, since the cylindrical portion 26 a is configured to have such a length along an axial direction of the spool shaft that the distal end of the cylindrical portion 26 a can be in close proximity to a side face of the friction disk 21 when the cover member 26 is fastened to the first flange portion 9 b, it is difficult for the friction disk 21 to wobble even when the brake disk 22 is separated from the friction disk 21.

The axial length of the engaging protrusions 26 e along an axial direction of the spool shaft is set such that a gap exists between the engaging protrusions 26 e and an outward facing surface of the first flange portion 9 b. Consequently, the distal ends of the engaging protrusions 26 e do not contact the outward facing surface of the flange portion 9 b when the cover member 26 is fastened to the flange portion 9 b and the gap between the cover member 26 and the storage space 36 can be reduced even further.

Constituent Features of the Spool Sound Generating Mechanism

As shown in FIG. 8 and FIG. 11, the spool sound generating mechanism 18 comprises a sound generating member 75, a striker member 76, a knob member 77, and a force applying member 78. The sound generating member 75 is fixed to an outward facing surface of the second flange portion 9 c of the spool unit 9. The striker member 76 is installed in the second side plate 13 b such that it can move freely toward and away from a sound generating position where it contacts the sound generating member 75 and a soundless position where it is separated from the sound generating member 75. The knob member 77 moves the striker member 76. The force applying member 78 applies a force acting to load the striker member 76 toward a neutral position.

The sound generating member 75 is made of, for example, a synthetic resin material and has a circular disk-shaped mounting portion 75 a fixed to the spool unit 9 and an undulated portion 75 b formed integrally with the mounting portion 75 a and having multiple gear tooth-like undulations formed on an external circumference thereof. The sound generating member 75 is arranged to rotate together with the spool 4.

The striker member 76 is made of, for example, a synthetic resin material and has a proximal end portion 76 a pivotally supported in the knob member 77, a striker portion 76 b that extends from the proximal end portion 76 a in a tapered shape that is narrow at a distal end and is contrived to repeatedly strike against the undulated portion 75 b, and a narrow neck portion 76 c formed between the proximal end portion 76 a and the striker portion 76 b. When the striker member 76 retracts to the soundless position, it is arranged in a portion where the second escape portion 19 f of the second cylindrical portion 11 b is formed. Consequently, the striker member can be arranged further outward in a radial direction than in a conventional reel and a larger sound generating member 75 can be used. Thus, a larger number of undulations can be provided on the undulated portion 75 b and a finer clicking sound can be generated.

The knob member 77 serves as an operating member for moving the striker member 76 to and from the sound generating position and the soundless position. The knob member 77 is a flanged shaft-like member having a shaft portion 77 a and a knob portion 77 b that is formed on a proximal end portion of the shaft portion 77 a and has a larger diameter than the shaft portion 77 a. The shaft portion 77 a is guided by an elongated hole 13 g passing from an outside surface to an inside surface of the second side plate 13 b. The striker member 76 is pivotally coupled to a distal end of the shaft portion 77 a.

The force applying member 78 is made of, for example, a synthetic resin material and has a C-shaped cylindrical spring portion 78 a having an opposing faces portion 78 c shaped like a place where a portion of a circle has been cut out and a plate-like mounting portion 78 b formed on an intermediate portion of the spring portion 78 a. The spring portion 78 a is configured such that when the striker member 76 advances to the sound generating position, the neck portion 76 c of the striker member 76 can contact the space of the opposing faces portion 78 c. A middle portion of the mounting portion 78 b has a fastening hole 78 d configured for a screw member 79 to pass through and a pair of positioning protrusions 78 e and 78 f provided on opposite sides of the fastening hole 78 d. The fastening hole 78 d is arranged such that it can align with a threaded hole 13 h that is formed in the inside surface of the second side plate 13 b and configured for the screw member 79 to screw into, and the positioning protrusions 78 e and 78 f engage with positioning holes 13 i and 13 j formed on opposite sides of the threaded hole 13 h. As a result, the force applying member 78 can be positioned more precisely and the number of parts can be reduced because the number of screw members used to fasten the force applying member can be reduced from two (the number used with a conventional force applying member) to one.

Procedure for the Setting Drag Force Adjustment Range

In a dual-bearing reel configured as described heretofore, the drag adjustment knob 51 is used to set a drag force adjustment range of the drag mechanism 6. When the drag adjusting knob 51 is rotated counterclockwise, it moves slightly leftward toward the state illustrated in the upper portion of FIG. 5 such that the drag force adjustment range is slightly weakened. Conversely, when the drag adjusting knob 51 is rotated clockwise, it moves slightly rightward toward the state illustrated in the lower portion of FIG. 5 such that the drag force adjustment range is slightly strengthened. More specifically, the drag adjustment range is adjusted such that a drag force will be produced when a weight having a prescribed mass is attached to the end of a fishing line and the fishing line is pulled while the drag adjusting lever 2 is in the strike position.

In order to adjust the strength of the drag force of the drag mechanism 6, a user rotates the drag adjusting lever 2. When the drag adjusting lever 2 is rotated fully toward the user to a drag release position indicated in FIG. 2 with a double-dot chain line, the cam receiving pins 52 a are arranged on the first flat surface 49 a in the drag release position shown in FIG. 10. If the drag adjusting lever 2 is rotated clockwise from the drag release position (clockwise from the perspective of FIG. 2), then the cam receiving pins 52 a move along the first slanted surface 44 c of the restricting protrusion 44 a of the cam surface 49 and reach the apex 44 b. Meanwhile, the weaker first force applying member 53 is compressed and the cam member 50 gradually moves outward along an axial direction of the spool shaft (rightward in FIG. 3) such that the spool shaft 5 and the spool 4 are gradually moved rightward (rightward in FIG. 3).

In a normal drag adjusting range, the friction disk 21 contacts the brake disk 22 and a drag force is generated when the cam receiving pins 52 a are positioned in front of the apex 44 b, i.e., on the first slanted surface 44 c, in a position lower than the lowest position of the curved second slanted surface 44 d. The drag force increases as the cam receiving pins 52 a move toward the apex 44 b of the restricting protrusion 44 a and then temporarily weakens when the cam receiving pins 52 a pass the apex 44 b. Once the cam receiving pins 52 a have passed the lowest position of the second slanted surface 44 d, the cam receiving pins 52 a contact the third slanted surface 49 c and the drag force begins to gradually increase. When the cam receiving pins 52 a reach the second flat surface 49 b, the drag force becomes the largest value in the drag adjustment range. During a pivot operation of the drag adjusting lever 2 toward the apex 44 b from the drag release position side, the drag force increases at a lower rate and the drag adjusting lever 2 is easier to operate because the slant angle of the first slanted surface 44 c is smaller than the slant angle of the second slanted surface 44 d (angle α<angle β).

If the drag adjusting lever 2 is rotated further clockwise (clockwise from the perspective of FIG. 2) after the brake disk 22 contacts the friction disk 21, then the Belleville springs constituting the second force applying member 54 will gradually compress as the spool shaft 5 moves. The drag force increases proportionally with a compression amount of the Belleville springs. When the strike position is reached, the cam receiving pins 52 a enters the recessed portions 49 f and the user experiences a small click-like feeling indicating that the drag adjusting lever 2 is in the strike position. When the drag adjusting lever 2 is in the strike position, a prescribed drag force is obtained in accordance with the adjustment of the drag adjusting knob 51. When the drag adjusting lever 2 is rotated beyond the strike position, the rate at which the drag force increases becomes smaller than prior to reaching the strike position. Finally, the drag force reaches the maximum value of the adjustment range when the cam receiving pins 52 a reach the second flat surfaces 49 b.

Conversely, when the drag adjusting lever 2 is rotated in the opposite direction (counterclockwise from the perspective of FIG. 2), the four Belleville springs constituting the second force applying member 54 and the coil spring constituting the first force applying member 53 spring load the spool 4 and the spool shaft 5 leftward from the perspective of FIG. 3 and the drag force gradually weakens. When the spring force exerted by the second force applying member 54 becomes weaker than the spring force exerted by the first force applying member 53, the friction disk 21 separates from the brake disk 22 and the drag mechanism enters a brake released state. When the cam receiving pins 52 a reach the restricting protrusion 44 a of the rotation restricting portion 44 during a counterclockwise operation of the drag adjusting lever 2, the drag force temporarily increases and the drag adjusting lever 2 becomes more difficult to rotate. Consequently, when the drag adjusting lever 2 is operated toward the drag release position, the drag adjusting lever 2 becomes more difficult to rotate (operate) just before it reaches the drag release position.

OTHER EXAMPLE EMBODIMENTS

(a) Although in the previously described embodiment a second facing portion 19 c and a second escape portion 19 f are also provided in the second opening 19 b where the drag mechanism 6 is not arranged, it is acceptable not to provide a second facing portion 19 c and a second escape portion 19 f because the length of the facing portion of the second opening and the second flange portion is short.

(b) Although in the previously described embodiment the first and second facing portions 19 c and 19 d are shortened by providing third and fourth escape portions 19 g and 19 h, it is acceptable not to provide the third and fourth escape portions 19 g and 19 h.

(c) Although the first and second facing portions 19 c and 19 d and the external circumferential surfaces of the first and second flange portions 9 b and 9 c are configured to be parallel to the spool shaft, the present invention is not limited to such a configuration. It is acceptable to configure the first and second facing portions or the external circumferential surfaces the first and second flange portions as cone-shaped surfaces arranged such that the diameters thereof increase in an axially outward direction. When such a cone-shaped surface is used, a centrifugal force generate by rotation of the spool causes a liquid entered into the gap to move more readily toward the first and second escape portions.

With the present invention, since the length of a portion of a first fishing line entry preventing part where the first opening and the first flange portion face each other is short, a liquid entering the gap there-between will flow more readily toward the first escape portion where the gap is wider. As a result, a liquid entering the gap between the first opening and the first flange portion will be less likely to inhibit the ability of the spool to rotate freely.

As used herein, the following directional terms “forward”, “rearward”, “above”, “below”, “downward”, “upward”, “radial”, “axial”, “inner”, “outer”, “longitudinal” and “transverse” as well as any other similar directional terms refer to those directions of a device equipped with the present invention. Accordingly, these terms, as utilized to describe aspects of the present invention, should be interpreted relative to a device equipped with the present invention.

The term “comprising” and its derivatives, as used herein, are intended to be open ended terms that specify the presence of the stated features, elements, components, groups, integers, and/or steps, but do not exclude the presence of other unstated features, elements, components, groups, integers and/or steps. The foregoing also applied to words having similar meanings such as the terms, “including,” “having,” and their derivatives. Also, the term “part,” “section,” “portion,” “member,” or “element” when used in the singular can have the dual meaning of a single part or a plurality of parts.

The terms of degree such as “substantially”, “about” and “approximately” as used herein mean a reasonable amount of deviation of the modified term such that the end result is not significantly changed.

The term “configured” as used herein to describe a component, section or part of a device implies the existence of other components, sections or parts necessary for that device to carry out a desired function.

While only selected embodiments have been chosen to illustrate the present invention, it will be apparent to those skilled in the art from this disclosure that various changes and modifications can be made herein without departing from the scope of the invention as defined in the appended claims. Furthermore, the foregoing descriptions of the embodiments according to the present invention are provided for illustration only, and not for the purpose of limiting the invention as defined by the appended claims and their equivalents. Thus, the scope of the invention is not limited to the disclosed embodiments. 

1. A lever drag type dual-bearing reel constructed to wind a fishing line around an axis transverse to a longitudinal direction of a fishing rod, the lever drag type dual-bearing reel comprising: a spool including a line winding body portion constructed to have a fishing line wound around the outer peripheral surface of the spool, a first cylindrical flange portion and a second cylindrical flange portion arranged on opposite ends of the line winding body portion, the diameter of the first and the second cylindrical flange portions being larger than the diameter of the line winding body portion; a spool shaft configured and arranged to rotatably support the spool; a drag mechanism including a brake disk that cannot rotate in a line reel-out direction, a friction disk attached to the first flange portion and constructed to rotate integrally with the spool so as to engage and disengage from the brake disk, and a moving mechanism configured to move the friction disk along the axial direction of the spool shaft relative to the brake disk; a drag adjusting lever configured to rotate about the spool shaft and arranged to adjust a drag force produced by the drag mechanism by controlling the moving mechanism; and a reel unit that supports the spool, the spool shaft, the drag mechanism, and the drag adjusting lever, the reel unit including a first end member with a first opening to receive the first flange portion, the first opening having an edge surface with a first facing portion facing towards the outer peripheral surface of the first flange portion, the first facing portion and the outer peripheral surface of the first flange portion defining a gap having an axial length shorter than the axial length of the outer peripheral surface of the first flange portion, and a first escape portion having a diameter larger than the first facing portion and arranged within the inner peripheral surface of the first end member, and a second end member arranged opposite to the first end member with a second opening to receive the second flange portion, the second opening having an edge surface with a second facing portion facing towards the outer peripheral surface of the second flange portion, the second facing portion and the outer peripheral surface of the second flange portion defining a gap having an axial length shorter than the axial length of the outer peripheral surface of the second flange portion, and a second escape portion having a diameter larger than the second facing portion and arranged within the inner peripheral surface of the second end member.
 2. The lever drag type dual-bearing reel according to claim 1, wherein the reel unit further including a third escape portion having a diameter larger than and arranged axially inward of the first facing portion, and a fourth escape portion having a diameter larger than arranged axially inward of the second facing portion.
 3. The lever drag type dual-bearing reel according to claim 1, wherein the diameter of the first flange portion is larger than the diameter of the second flange portion, and the diameter of the first opening is larger than the diameter of the second opening.
 4. The lever drag type dual-bearing reel according to claim 1, wherein the outer peripheral surface of the first flange portion is longer in the axial direction than the outer peripheral surface of the second flange portion, the first flange portion defining a storage space to accommodate the friction disk and the brake disk.
 5. The lever drag type dual-bearing reel according to claim 4, wherein the drag mechanism further including a cover member configured and arranged to cover the storage space. 